JP3183237B2 - Vibration device for variable vibration table - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a vibrating device for a variable amplitude type vibration table suitable for a vibration table which generates only vertical vibration used in a block molding machine or the like.

[0002]

2. Description of the Related Art In general, there have been known various types of vibrating apparatuses that vibrate a vibration table with a vibration shaft having an eccentric weight. For example, as a vibration table in a concrete block molding machine, as shown in Japanese Patent Application Laid-Open No. 2-80203, the position of the weight portion is hydraulically positioned at the lower surface position of the vibration table body that receives the formwork filled with the block material. Two vibration shafts with a double shaft configuration that can be directly changed are arranged,
There is one in which the position of the weight is moved by sliding each hydraulic piston to change the amplitude.

[0003]

However, in a vibration mechanism having a dual-shaft configuration in which one shaft is an inner cylinder and an outer cylinder, the structure is too complicated to perform the vibration unbalance position with a phase shift. Therefore, it is difficult to control the position of the weight portion, it is not easy to incorporate the weight into the device, and the maintenance is troublesome.

[0004] Further, two vibration shafts having a double shaft configuration previously proposed by the applicant of the present application are incorporated in the center of the vibration table, and this inner cylinder shaft is formed as an unbalanced shaft having a weight structure. There is a vibration device that provides a torsional cam groove on the balance shaft and mechanically moves a control pin fitted into the torsional cam groove in the longitudinal direction to change the phase of the weight portion to obtain a predetermined vibration. In addition, the sliding of the control pin with respect to the torsional cam groove is not smooth, and a shift or the like is apt to occur, and it is difficult to obtain a uniform predetermined vibration over the entire vibration table.

In view of the above-mentioned circumstances, the present invention relates to a construction in which two vibration shafts with eccentric weights for inducing vibration are paired.
A simple type of variable vibration that solves the above-mentioned problem by symmetrically disposing the eccentric weights of one of the vibration axes of each set in the vibration table of each set symmetrically in the vibration table. It is an object of the present invention to provide a table vibration device.

[0006]

According to the present invention, a pair of vibration source shafts with equivalent eccentric weights, which are driven by independent motors and synchronized with each other, are arranged in parallel in a predetermined vibration table. A vibration driven shaft with an eccentric weight equivalent to the equivalent eccentric weight, whose phase can be changed in parallel with the shafts, is arranged on the bearing to form a quadruple shaft configuration, and a toothed pulley provided at each end of the vibration driven shaft The timing belts to be hung are passed over the toothed pulleys at the ends of the respective vibrating shafts via toothed tension pulleys arranged at the upper and lower ends of a swing support arm having the center pivoted, respectively, to form a symmetrical reverse transmission mechanism, And, the pivots of the left and right opposing swing support arms are connected to an interlocking link mechanism controlled by a single cylinder for symmetrical rotation, and only the vertical amplitude of the vibration table from the maximum to the minimum according to the extension amount of the cylinder rod. It is made to be variable .

In this case, the interlocking link mechanism arranges the pivot of one swing support arm in the middle of the crank connected to the rod end of the cylinder, and connects the connecting rod end connected to the tip of the crank to the other swing. It is connected to an interlocking rod end arranged on the pivot of the dynamic support arm.

[0008] The invention described in claim 2 is the first invention.
The cylinder rod described in (1) above can be extended freely during vibration of the vibration table and continuously varies.

As described above, the vibrating apparatus has two vibrating shafts with equivalent eccentric weights that rotate synchronously and two vibrating slave shafts with eccentric weights whose phase can be changed from that of the eccentric weights of the vibrating shaft. A total of 4
Using the vibration axes, and each of the vibration slave axes are symmetrically reversely rotated from the vibration original axis via a timing belt,
The phase change of the eccentric weight on the side of the vibration driven shaft is linked to a single cylinder in a stepless manner via an interlocking link mechanism. Two sets of oscillating shaft with weight and oscillating slave shaft with eccentric weight are symmetrical, and only vertical vibration from maximum to minimum due to selection of phase of eccentric weight of both oscillating shaft and slave shaft appear.

That is, when the position (phase) of the eccentric weight of each vibration driven shaft is set to be vertically symmetrical with respect to the equivalent eccentric weight of each vibration original shaft, the vibration in the vertical direction will be reduced. And the eccentric weight of the vibration slave shaft are vertically symmetrical and offset by symmetrical positions, and have a minimum amplitude. Horizontal (horizontal) vibration is 2 degrees with respect to the center of the table.
Since the set vibration source axis and the vibration slave axis are symmetrically arranged, they are offset to zero.

When the position (phase) of the eccentric weight of each vibration driven shaft is set in the same direction as the equivalent eccentric weight of each vibration original shaft, the amplitude in the vertical direction is maximized. In all phases from the minimum to the maximum amplitude, the horizontal vibration is 2
Since the equivalent eccentric weight of the pair of vibration original shafts and the eccentric weight of the vibration slave shaft are bilaterally symmetric and equivalent, the vibration in the horizontal direction is canceled and becomes zero.

In this vibration table, the amplitude in the vertical direction can be continuously varied from the maximum to the minimum (stop) by moving the position of the equivalent eccentric weight of the left and right vibration slave axes. However, in the case of horizontal vibration, the two sets of the vibration slave shaft with eccentric weight and the vibration original shaft with eccentric weight are symmetrical with respect to the table center.
Even if the position of the eccentric weight changes, the symmetry is maintained as a whole, and the vibration in the horizontal direction is canceled out, so that only the amplitude in the vertical direction occurs.

[0013]

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a perspective view of a vibration device for a variable vibration table according to the present invention.

FIGS. 1 to 6 show an embodiment using an oscillating shaft in which an eccentric weight (weight) is attached to one surface in the longitudinal direction of a rotating shaft. Reference numeral 1 denotes a vibration source shaft having a pair of equivalent eccentric weights 4 disposed in parallel with bearings 3 at right and left positions with respect to the center of a predetermined vibration table 2, and each vibration source shaft 1 is an independent motor 5. It is driven via a belt 6, and the synchronous gears 7 provided at the respective shaft ends are meshed with each other to rotate synchronously. Numeral 8 denotes a vibrating slave shaft having eccentric weights 9 which are disposed parallel to each other on the outer side of each of the vibration source shafts 1 and which are equivalent to each other. An appropriate phase can be obtained for the equivalent eccentric weight 4 of the vibration original shaft 1 by movement. The rotation of each of the vibration driven shafts 8 is reversed from each of the vibration original shafts 1 via an appropriate transmission mechanism. The structure of the reverse rotation transmission mechanism 10 is such that an endless double-sided timing belt 12 hung on a toothed pulley 11 provided at the shaft end of a vibration driven shaft 8 is integrally attached to a bearing 14 on a machine body 13 and a support shaft 15 of a bearing. Swing support arm 1
6 is mounted on the upper and lower parts of the vibration source shaft 1 and 17 'to be inverted, and both sides are mounted on a toothed pulley 18 having the same number of teeth as the toothed pulley 11 mounted on the shaft end of the vibration original shaft 1. The vibration slave shaft 8 and the vibration original shaft 1 are rotated in reverse.

Reference numeral 19 denotes an interlocking link mechanism for symmetrically interlocking the pair of left and right vertically used swing support arms 16, 16. The interlocking link mechanism 19 connects the rod shaft 20 a of the single cylinder 20 to the body 13. One of the shafts 15 of the bearing is connected to the lower end of a crank portion 21 disposed at the center of the bearing 14 ′ on the side, and the tip of a connecting rod 22 connected to the upper end of the crank portion 21 is connected to the other bearing 14. The crank structure is connected to the lower end of the swinging rod 23 provided on the support shaft 15 of the bearing, and the entire structure constitutes a vibrating device 24 for a variable vibration table.
In the figure, reference numeral 25 denotes a cushioning member mounted between the body 13 and the vibration table 2.

Now, the operation will be described. The vibration device 24 for a variable vibration table is incorporated in a concrete block forming machine 26 as shown in FIG. 7, for example. In this case, the vibration device 24 is mounted on the vibration table 2 on which the block formwork 27 is placed. A stamping / pressing unit 28 is disposed above the vibration table 2, and hopper units 29 and 29 'for feeding two types of raw materials to the left and right sides of the mold position.
Has been arranged.

Here, as the molding of the concrete block, block raw materials a and a 'fed from the hoppers 29 and 29' are sequentially filled in a predetermined formwork 27, and a predetermined vibration is applied to the vibration table 2. The embossing / pressing unit 28 is lowered while being applied to form a concrete block.

Here, the vibration generated in the vibration table 2 is:
The equivalent eccentric weights 4 of the two vibrating shafts 1 are arranged at the same position among the four vibrating shafts supported on the vibrating table 2. Since the set position (phase) of the eccentric weight 9 is variable by the operation of the reverse transmission mechanism 10 and the interlocking link mechanism 19 from the same position to the equivalent eccentric weight 4 to a symmetrical position shifted by 180 ° from the equivalent eccentric weight 4, the equivalent eccentric weight 9 is changed. By selecting the phase of the eccentric weight 4 and the eccentric weight 9, vibration in the range from the maximum amplitude to the minimum amplitude is obtained.

For example, when the eccentric positions of the eccentric weights 9 of the two vibration driven shafts 8 which are parallel to the eccentric positions of the equivalent eccentric weights 4 of the two vibration original shafts 1 are the same (see FIGS. 3 and 3). 6 C),
In the vertical direction, the vibration is amplified and a vertical vibration of the maximum amplitude is generated. At this time, the vibration in the horizontal direction is such that two sets of the vibration original shaft 1 with the equivalent eccentric weight 4 and the vibration slave shaft 8 with the eccentric weight 9 are symmetrical with respect to the left and right positions with the table center as the center. As a result, both vibrations cancel each other out, resulting in zero horizontal vibration.

If it is desired to change the vertical vibration of the vibration table 2 due to each step of material supply, compression, etc., or the molding height, raw materials (heavy aggregate, lightweight aggregate), etc., the equivalent eccentric weight is used. The phases of the eccentric weights 4 and 9 may be shifted by an appropriate angle from the state of the vibration original shaft 1 and the oscillating slave shaft 8 with eccentric weight. As the turning operation of the eccentric weight 9, first, the cylinder 20 is appropriately operated and its rod shaft 20a is extended, and the crank portion 21 at the end of the rod shaft 20a rotates sideways with the support shaft 15 as a fulcrum. Connecting rod 2 at the tip of the part 21
Oscillating slave shaft 8 with eccentric weights that are interlocked and oppose at symmetrical positions
The swinging rod 23 is rotated, and the support shaft 1 integrated with the swinging rod 23 is rotated.
The swinging support arm 16 is interlocked via 5.

Here, when the extension amount of the cylinder rod shaft 20a is maximized, the swing support arm 16 and the swing support arm 16 opposite to each other are shown in FIG. 2 due to the rotation of the support shafts 15 and 15, respectively. As shown in FIG. At this time, toothed pulleys 17 and 17 ′ provided at the upper and lower ends of each swing support arm 16.
The middle and upper toothed pulleys 17 move toward the toothed pulley 11 of the vibration driven shaft 8, and the lower toothed pulley 17 ′ moves away from the toothed pulley 11. 2, the right vibration slave shaft 8 rotates counterclockwise and the left vibration slave shaft 8 rotates clockwise in FIG. The eccentric weight 9 faces a symmetrically displaced position rotated by 180 ° with respect to the equivalent eccentric weight 4 of the vibration original shaft 1.

As described above, if the eccentric weight 9 of the vibration driven shaft 8 and the eccentric weight 4 of the vibration original shaft 1 face vertically symmetrical positions, both vibrations generated in the vibration driven shaft 8 and the vibration original shaft 1 are generated. Are offset.
That is, under this condition, the amplitude in the vertical direction becomes minimum. Of course, the horizontal vibrations at this time are also totally symmetrical with respect to the center position of the vibration table 2 because the two sets of the vibration slave shaft 8 and the vibration original shaft 1 are arranged symmetrically with respect to the center position of the vibration table 2. You. That is, the horizontal vibration becomes zero.

If the amount of extension of the rod shaft 20a of the cylinder 20 is stopped at an appropriate intermediate position between the maximum extension and the minimum extension, the eccentric weight 9 of the vibrating slave shaft 8 will The phase is arbitrarily shifted left and right with respect to the equivalent eccentric weight 4, and the vertical amplitude becomes an arbitrary amplitude between the maximum, the minimum, and the middle. At this time, basically, the vibration in the horizontal direction is zero. That is, this type of vibration table 2 generates vibration only in the vertical direction. For example, cylinder 2
If the extension amount of the rod shaft 20a of 0 is stopped at the intermediate position,
The eccentric weight 9 of the vibration driven shaft 8 is the equivalent eccentric weight 4 of the vibration original shaft 1.
, The phase is shifted by 90 °, and an intermediate amplitude between the maximum and minimum amplitudes is obtained.

The principle of the vibration will be described in detail with reference to FIG. 6. As shown in FIG. 6A, two sets of vibration original shafts 1A and 1B with equivalent eccentric weights and a vibration slave shaft with eccentric weights are used. 8A, 8
B is symmetrically arranged at the left and right positions in the vibration table, and the equivalent eccentric weights 4A and 4B of the vibration original shafts 1A and 1B
Are located at the same position below, and the positions of the eccentric weights 9A and 9B of the vibrating slave shafts 8A and 8B on both outer sides are 180 ° out of phase (opposite positions) with respect to the eccentric weights 4A and 4B. 2
The set of eccentric weights 4A (4B) of the vibration source shafts 1A (1B) and the eccentric weights 9A (9B) of the vibration slave shafts 8A (8B) are symmetrical at opposite positions. Shaft 8A, 8
If B vibrates, both vibrations are canceled and the amplitude in the vertical direction becomes minimum. At this time, as the vibration in the horizontal direction, the eccentric weights 4A, 4B and 9A, 9B of the two sets of vibration original shafts 1A, 1B and the vibration driven shafts 8A, 8B have a symmetrical and equivalent arrangement as a whole. The vibration in the left-right direction is canceled, and the vibration in the horizontal direction becomes zero.

As shown in FIG. 6 (C), the eccentric weights 4A and 4A of the pair of vibration original shafts 1A and 1B are located at the left and right positions.
B is located at the same position on the lower side, and the eccentric weights 9A and 9B of the vibrating slave shafts 8A and 8B on both outer sides are also at the same position on the lower side, the vibration original shafts 1A and 1B and the vibrating slave shafts 8A and 8B When rotated, the vibration is amplified and the maximum amplitude is obtained in the vertical direction.
At this time, the vibration in the left-right direction is canceled out due to the symmetrical arrangement of the center of the table as a whole, as described above, and the vibration in the horizontal direction is also zero.

As shown in FIG. 6B, the eccentric weight 9
When the phases of A and 9B are set at an intermediate position with respect to the above-described aspect,
That is, the eccentric weights 9A and 9B of the vibration driven shafts 8A and 8B are 90 ° from the positions of the eccentric weights 4A and 4B of the vibration original shafts 1A and 1B.
When the phase shift of FIG.
6 (A) and the minimum amplitude shown in FIG. 6 (A). This means that a desired value of the vertical amplitude of the table from the maximum value to the minimum value can be obtained by selecting the setting positions of the eccentric weights 9A and 9B of the oscillation slave shafts 8A and 8B.

[0027]

As described above, the vibrating device for a variable vibration table according to the present invention comprises a pair of synchronized vibrating shafts with eccentric weights, and eccentric weights whose phases can be changed on both sides thereof. A four-shaft configuration having a vibration driven shaft attached thereto, wherein the rotation of each vibration driven shaft is reversely transmitted through tension pulleys arranged at the upper and lower ends of a swing support arm with a timing belt from the vibration original shaft, and the swing support arm Is connected to an interlocking link mechanism controlled by a single cylinder and swings, and the oscillating slave shaft itself is rotated with a timing belt shift according to the movement of the tension pulley position above and below the swing support arm, and the eccentric weight Since the position is shifted to cause a phase shift with respect to the eccentric weight of the vibration original shaft, if this device is incorporated in a vibration table, only the vertical amplitude can be continuously changed from the maximum to the minimum in the vibration table. Depending on the purpose of use It can give the upper and lower vibration.
That is, the point that this vibrating device for a vibrating table can be changed during operation only by the operation of a single cylinder can be adjusted at any time according to the size and process of the raw material and the molded product.

Further, at this time, since the vibration change at this time is easy only because the reverse rotation transmission mechanism and the interlocking link mechanism that hang the timing belt are linked by a single cylinder, the handling is easy, and the amplitude can be changed during the vibration operation of the vibration table. . Further, if the cylinder itself is at least outside the vibration table, it is possible to visually monitor the change in vibration, and the amount of vibration only in the vertical direction can be easily determined only by looking at the amount of extension of the cylinder rod shaft.

This means that, for example, when a vibration table of a concrete block molding machine is used, the amplitude is instantaneously switched to the optimum amplitude corresponding to each step of material supply, filling, compression and the like to the formwork, and the expected time is shortened in the shortest time. Can achieve the purpose of
It is most suitable for the case where the productivity is improved and the vibration is changed according to the difference of the block raw material and the like.

Further, in the present invention, since the four vibration source shafts with eccentric weights are simply connected in parallel to the vibration table in parallel, the whole vibration mechanism is simplified, so that it can be mounted on various vibration tables. And maintenance is also facilitated.

[Brief description of the drawings]

FIG. 1 is a perspective view showing a main part of an embodiment of a vibration device for a variable vibration table according to the present invention.

FIG. 2 is a side view showing the main part when the amplitude in the vertical and horizontal directions is minimized.

FIG. 3 is a side view showing the main part when the amplitude in the vertical direction is maximized and the vibration in the horizontal direction is zero.

FIG. 4 is an explanatory diagram showing a reverse rotation transmission mechanism that makes the axial position of a vibration slave shaft variable.

FIG. 5 is an explanatory diagram of an interlocking link mechanism for interlocking the reverse rotation transmission mechanism.

FIG. 6 is a diagram showing a positional relationship between an eccentric weight of a vibration source shaft and a vibration slave shaft in a quadruple series, and FIG. 6A is a vertical symmetric diagram of an equivalent eccentric weight of the vibration source shaft and an eccentric weight of a vibration slave shaft. FIG. 4B is an explanatory view in which the amplitude in the vertical direction is set to the minimum position, and FIG.
FIG. 4C is an explanatory diagram in which the vertical phase amplitude is set to the middle amplitude while the phase is shifted, and the equivalent eccentric weight of the vibration source shaft and the eccentric weight of the vibration slave shaft are set at the same position below, respectively. It is explanatory drawing which maximizes the vibration of a direction.

FIG. 7 is an explanatory view showing an embodiment in which a vibration device for a variable vibration table is incorporated into a vibration table of a concrete block molding machine.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Vibration original shaft 2 Vibration table 4 Equivalent eccentric weight 5 Motor 8 Vibration slave shaft 9 Eccentric weight 10 Reverse rotation transmission mechanism 11 Toothed pulley 12 Timing belt 16 Oscillating support arm 17, 17 'Toothed pulley 18 Toothed pulley 19 Interlocking link mechanism 20 Cylinder 21 Crank part 22 Continuous rod 23 Swing rod

Claims (2)

(57) [Claims] 1. A pair of equivalent eccentric weight-equipped vibration original shafts driven and synchronized by independent motors in parallel in a predetermined vibration table, and the equivalent eccentricity is provided in parallel with each of the vibration original shafts. The oscillating driven shafts with eccentric weights whose phases can be changed from the weighing weights are arranged on the bearings to form a quadruple-shaft configuration, and the timing belts to be hung on the toothed pulleys provided at the ends of the oscillating driven shafts are respectively centered. A symmetrical reverse transmission mechanism is formed to extend over the toothed pulleys at the ends of the respective vibration original shafts via toothed tension pulleys arranged at the upper and lower ends of a swinging support arm pivotally attached to the swinging support arm, and the left and right opposing swinging supports are formed. An arm pivot connected to an interlocking link mechanism controlled by a single cylinder , and
Link mechanism is connected to the rod end of the cylinder.
The pivot axis of one swing support arm is arranged in the middle of the
Connect the end of the connecting rod to the tip of the link
The pivoting arm of the left and right opposing swing support arms is
A vibrating device for a variable vibration table , wherein only a vertical amplitude of the vibration table is varied from a maximum to a minimum in accordance with an extension amount of the cylinder rod by connecting the shafts so as to rotate symmetrically. . 2. The vibration table according to claim 1, wherein the cylinder rod is a vibration table.
It is characterized by being able to be fed out inside and making continuous adjustment
The vibration device for a variable vibration table according to claim 1.